EP0000517B1 - Dichtungsmanschette - Google Patents

Dichtungsmanschette Download PDF

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Publication number
EP0000517B1
EP0000517B1 EP78100392A EP78100392A EP0000517B1 EP 0000517 B1 EP0000517 B1 EP 0000517B1 EP 78100392 A EP78100392 A EP 78100392A EP 78100392 A EP78100392 A EP 78100392A EP 0000517 B1 EP0000517 B1 EP 0000517B1
Authority
EP
European Patent Office
Prior art keywords
angle
cup
cylinder
piston
inclined portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP78100392A
Other languages
English (en)
French (fr)
Other versions
EP0000517A1 (de
Inventor
Junzo Hasegawa
Masatoshi Yamada
Kaoru Nakamura
Eiichi Yasuda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Toyota Central R&D Labs Inc
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Toyota Motor Corp
Toyota Central R&D Labs Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd, Toyota Motor Corp, Toyota Central R&D Labs Inc filed Critical Aisin Seiki Co Ltd
Publication of EP0000517A1 publication Critical patent/EP0000517A1/de
Application granted granted Critical
Publication of EP0000517B1 publication Critical patent/EP0000517B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/324—Arrangements for lubrication or cooling of the sealing itself

Definitions

  • This invention generally relates to a sealing cup as described on the preamble of claim 1 and adapted for use in vehicular devices, and more particularly to improvements in a sealing cup to be mounted on any piston and cylinder for producing a fluid pressure and for fluidtightly sealing the same.
  • the brake device of these days has to satisfy the following requirements to provide an improved brake cup; that the brake pedal will be smoothly depressed with little resistance and that the vehicle can be stopped by a small depression of the brake pedal.
  • one of the major drawbacks of the conventional brake cup is, although satisfactory as regards the sealing, that it is obliged to increase the resistance of slide due to shortage of the oil film formed between the slide surfaces. Therefore, a large foot force is necessary to pressurize the brake fluid, causing a poor pressurizing efficiency of brake fluid.
  • a stable movement of the piston provided with the conventional brake cup will. not be secured due to possible vibration like stickslip vibration with the result of unstable brake application.
  • FIG. 1 to 4 wherein so- called ring cups are illustrated; cups of Figs. 1 and 3 are called S.A.E type while the cups of Figs. 2 and 4 are called Opel type.
  • Each of these conventional ring cups comprises an outer lip 1 substantially similar to the frustum of a cone, an inner lip 2, and a base 3.
  • S.A.E type cup of Figs. 1 and 3 comprises a tip 9 at the maximum diameter portion of the outer lip 1 at which the maximum pressure is applied by contact of the cup with a cylinder 12.
  • a piston cup of the invention comprises an outer lip 1 with an outer sealing surface 4 at its leading end 5 with an inclined portion 6.
  • the angle a of the inclined portion 6 relative to the axis parallel to the cylinder axis is smaller when unmounted than the angle 0 of the remaining portion of the sealing surface to the said axis, its value being determined as 1 ° ⁇ ⁇ 15°.
  • the tip 9 is at a position where the outer diameter of the piston cup is larger than the inner diameter of the cylinder.
  • a flash free and smooth wedge-shaped clearance is constituted between the inclined portion 6 and the cylinder wall to form an oil film therebetween when the piston cup slides on the cylinder wall.
  • the slide resistance of the cup will be decreased to realize various advantages such as a stable movement of the piston, improvement in the pressure increasing efficiency, and improvement in the durability of the cup.
  • the piston cup of Fig. 7(A) comprises an inner sealing surface 8 at the inner lip 2 which includes a portion smaller in diameter than the outer diameter of the piston and the outer sealing surface 4 at the outer lip 1 which includes a portion larger in diameter than the inner diameter of the cylinder. Consequently, the piston cup receives bending force at the inner lip 2 thereof and at the outer lip 1 thereof when installed within the cylinder 12 as shown in Fig. 7(B).
  • the sealing pressure of the cup in contact with the cylinder 12 and the piston 11 is illustrated in Fig. 7C.
  • Fig. 7(B) shows that the leading edge 10 of the outer lip 1 is being apart from the cylinder wall.
  • Fig. 8(B) shows that the leading edge 10 is in contact with the cylinder wall when the piston cup is installed and Fig. 8(C) shows that when the inner pressure is applied the leading edge is apart from the cylinder wall and the pressure at a portion of the edge is below the inner pressure.
  • the fluid wedge operation of the piston cup having the inclination angle ⁇ (Fig. 9(A)) when mounted has been proved effective in the fluid lubrication theory, i.e. the minimum thickness of the fluid film should be a few microns to dozens of microns in order to realize the fluid wedge operation in the most effective way, so that the inclination angle ⁇ is a few degrees.
  • the angle a preferably be designed as 1 1 ⁇ ⁇ 7° from Fig. 9(B). It is to be noted in Fig. 9(B) that the angle ⁇ may be designed as 1 ° ⁇ a ⁇ 10° in order to accomplish the fluid wedge effect.
  • Fig. 10 shows the test results of slide resistance with the angle ⁇ being different -30 0 , -10 0 , and 5° when the length I of the inclined portion 6 is nearly equal to 0.15 x L (L: length of the sealing surface 4) and the angle 0 is 15°.
  • the angle 0 may be varied within the range of 10° ⁇ 0 ⁇ 30°.
  • the angle ⁇ of the inclined portion may be 1 ° ⁇ 15° so as to realize the fluid wedge effect.
  • the minimum limit of the angle range should be ⁇ 1 0 and the decrease of the angle a (the increase of the absolute value of the angle a) will not realize the fluid wedge effect.
  • the major factors for accomplishing the fluid wedge operation are the angle, the shape, and the size of the clearance formed between the inclined portion of the piston cup and the cylinder (or the piston) when the cup is installed between the cylinder and the piston.
  • the shape and the size of the clearance are primarily determined by the angle of the inclined portion 6 of the lip and the pressure applied to the inside of cup, and secondarily by the tightening clearance of the cup, and the shape and the elasticity of the portion other than the inclined portion thereof.
  • Figs. 13 and 14 show the piston cup of the invention which is being used as secondary cup of the brake device. At first the brake master cylinder will be explained with reference to Fig. 13.
  • the tandem master cylinder CY comprises a first piston Pl and a second piston P2 each slidably fitted therein.
  • the first piston Pl is provided with a secondary cup SC and a primary cup PC1.
  • the second piston P2 is provided with a primary cup PC2 and floating cups FC1 and FC2.
  • a fluid chamber RC of the rear wheel side is pressurized.
  • the second piston P2 is also moved left due to pressure in the chamber RC so that the primary cup PC2 closes a compensation hole CH2, fluidically connected to a reservoir tank RT2 thereby pressurizing fluid chamber FC of the front wheel side.
  • the secondary cup SC mounted on the first piston P1 serves to seal between the inside of the cylinder CY and the outside thereof.
  • the primary cups PC1 and PC2 of the pistons P1 and P2 serve to receive the fluid pressure.
  • the floating cups FC1 and FC2 serve to seal between the rear side chamber RC and the front side chamber FC.
  • the secondary cup SC comprises an outer lip 1 having an unbroken curve at the outer periphery thereof, and an inclined portion 6 at the end thereof.
  • the inclined portion 6 has an inclination angle 5° with respect to the line passing a point 9 and being parallel to the cylinder axis.
  • Fig. 15 shows the piston cup of the invention which is used as a primary cup of the brake device.
  • the primary cup comprises an inclined portion 6 on its outer lip 1 (the angle a of the inclined portion is 1°).
  • the wedge-shaped clearance is similarly formed upon sliding movement of the primary cup so as to decrease the slide resistance.
  • the piston cup of the invention may be used as primary cup of the clutch device.
  • the piston cup of the invention may be employed in a proportioning valve device which will increase the wheel brake pressure with a reduced ratio relative to the master brake pressure.
  • the piston cup used in the proportioning valve device There are two kinds of the piston cup used in the proportioning valve device; in one of which the outer lip of the cup slides with respect to the inner wall of cylinder and in the other of which the inner lip of the cup slides with respect to the outer wall of the piston.
  • the applicants of the invention have found that the inclined portion angle a of any cup should be 1 ° ⁇ a ⁇ 15° so as to effect the fluid wedge operation in the most effective way. Otherwise, the angle ⁇ of the cup may be 1 ° ⁇ 7° in consideration of the inner pressure applied thereto and the tightening clearance thereof.
  • Fig. 16 shows a modified embodiment of the present invention in which a chamfered surface 13 is provided on the inclined portion of the sealing cup.
  • the surface 13 is inclined with respect to a line (L) in the direction opposite to the inclination indicated by a and such the inclination is designated by ⁇ ' in Fig. 16.
  • ⁇ ' in Fig. 16.
  • the angle ( ⁇ ') is selected from the range of 0° to 45°.
  • the preferable range of the angle (a') is 15° to 45°.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Claims (6)

1. Dichtungsring für eine hydraulische Vorrichtung mit Kolben und Zylinder, bei der die Dichtung mit ihrer hohlen Seite beim Arbeitshub der Vorrichtung in Richtung auf das im Zylinder enthaltene Fluid bewegt wird und der die folgenden Merkmale besitzt:
Einen Ringkörper aus nachgiebigem Material mit einer Kreisringbasis (3),
eine von der Kreisringbasis vorstehende ringförmige innere Dichtungslippe (2), die eine nach innen geneigte innere Dichtungsfläche (8) hat, die sich an eine abzudichtende Wandung anlegen kann und
eine von der Kreisringbasis (3) vorstehende ringförmige, die innere Dichtungslippe (2) im Abstand umgebene äußere Dichtungslippe (1), die eine äußere Dichtungsfläche (4) hat, die mit einer abzudichtenden Wandoberfläche zusammenwirken kann, wobei von der inneren und äußeren Dichtungsfläche eine gegenüber der entsprechenden Kolben- (11) bzw. Zylinderwand (12) verschiebbar ist, und
einen an einem Vorderende der ringförmigen inneren und/oder äußeren Dichtungsfläche (4; 8) vorgesehenen ringförmigen geneigten Abschnitt (6), der an seiner Vorderkante gratfrei
und eben ist und sich in Umfangsrichtung erstreckt, dadurch gekennzeichnet, daß der Winkel α des ringförmigen geneigten Abschnitts (6) gegen die Achse des Zylinders (12) kleiner als der Winkel 0 des anderen Abschnitts der zugeordneten Dichtungsfläche (4) zur Achse ist und wie folgt festgelegt ist:
Figure imgb0012
wobei nach Einbau des Dichtungsringes zwischen dem Zylinder und dem Kolben der geneigte Abschnitt (6) so geneigt ist, daß er einen keilförmigen Freiraum bildet und Fluid, wie z. B. Öl, an eine Gleitfläche von mindestens dem Zylinder oder dem Kolben leitet.
2. Dichtungsring nach Anspruch 1, dadurch gekennzeichnet, daß an dem Vorderende des geneigten Abschnitts (6) eine Schrägfläche (13) vorgesehen ist, deren Winkel a' gegen die Zylinderachse negativ zu dem Winkel a des geneigten Abschnitts (6) und größer als derjenige des geneigten Abschnitts ist, und wie folgt festgelegt ist:
Figure imgb0013
3. Dichtungsring nach Anspruch 1, dadurch gekennzeichnet, daß der Winkel α des ringförmigen geneigten Abschnitts (6) wie folgt festgelegt ist:
Figure imgb0014
4. Dichtungsring nach Anspruch 1, dadurch gekennzeichnet, daß der Winkel α des ringförmigen geneigten Abschnitts (6) zu dem Winkel 0 des anderen Abschnitts (7) der ringförmigen inneren und/oder äußeren Dichtungsfläche gegenüber der Zylinderachse im folgenden Verhältnis steht:
Figure imgb0015
5. Dichtungsring nach Anspruch 2, dadurch gekennzeichnet, daß der Winkel a' der Schrägfläche (13) wie folgt festgelegt ist:
Figure imgb0016
6. Dichtungsring nach Anspruch 2, dadurch gekennzeichnet, daß der Winkel a des ringförmigen geneigten Abschnitts (6) 5° und der Winkel a' der Schrägfläche (13) -30° beträgt.
EP78100392A 1977-07-15 1978-07-13 Dichtungsmanschette Expired EP0000517B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP95011/77 1977-07-15
JP1977095011U JPS5835892Y2 (ja) 1977-07-15 1977-07-15 ピストンカツプ

Publications (2)

Publication Number Publication Date
EP0000517A1 EP0000517A1 (de) 1979-02-07
EP0000517B1 true EP0000517B1 (de) 1981-05-13

Family

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Family Applications (1)

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EP78100392A Expired EP0000517B1 (de) 1977-07-15 1978-07-13 Dichtungsmanschette

Country Status (4)

Country Link
US (1) US4189160A (de)
EP (1) EP0000517B1 (de)
JP (1) JPS5835892Y2 (de)
DE (1) DE2860697D1 (de)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4258927A (en) * 1978-12-13 1981-03-31 Garlock Inc. Shaft seal with retractable polytetrafluoroethylene-lined sealing lip
US4867043A (en) * 1986-06-30 1989-09-19 Tayco Developments, Inc. End cap for fluid cylinder
US5169286A (en) * 1989-03-09 1992-12-08 Yutaka Yamada Variable capacity centrifugal water pump with movable pressure chamber formed by impeller
DE19505012A1 (de) * 1995-02-15 1996-08-22 Teves Gmbh Alfred Dichtmanschette für hydraulische Anlagen
US5575484A (en) * 1995-06-30 1996-11-19 Greene, Tweed Of Delaware, Inc. Fluid pressure activated piston return spring seal
DE10028672A1 (de) * 2000-06-09 2001-12-13 Fte Automotive Gmbh Dichtelement für hydraulische Kolben-Zylinder-Anordnungen
JP4699594B2 (ja) * 2000-10-10 2011-06-15 カヤバ工業株式会社 流体圧用パッキン

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA529112A (en) * 1956-08-14 The Garlock Packing Company Of Canada Sealing devices
US2664952A (en) * 1948-03-15 1954-01-05 Guiberson Corp Casing packer cup
US2686402A (en) * 1948-12-31 1954-08-17 Charles A Samuel Hydraulic brake wheel cylinder piston
US2720924A (en) * 1950-02-20 1955-10-18 Cicero C Brown Connecting devices for well tools
US2884291A (en) * 1953-10-05 1959-04-28 Kelsey Hayes Co Sealing cup
US2815995A (en) * 1954-06-28 1957-12-10 Acushnet Process Company Lip type seal for sealing hydraulic and pneumatic pressure systems
US2867457A (en) * 1954-07-16 1959-01-06 Gen Motors Corp Fluid seal
DE1046966B (de) * 1956-04-30 1958-12-18 Freudenberg Carl Kg Lippendichtung
GB944921A (en) * 1959-01-10 1963-12-18 Girling Ltd Improvements in seals
GB1019523A (en) * 1964-01-22 1966-02-09 Angus George Co Ltd Improvements in and relating to packing rings
US3527507A (en) * 1968-02-12 1970-09-08 Garlock Inc Unitary bearing element with improved,integral scraper-sealing lip
DE2002082A1 (de) * 1969-11-26 1971-06-03 Mini U Generaldirektor Der Deu Lippendichtring fuer Luftkupplungen
US3653670A (en) * 1970-05-11 1972-04-04 Cascade Corp Spring-loaded seal with symmetrical cross section

Also Published As

Publication number Publication date
JPS5835892Y2 (ja) 1983-08-12
DE2860697D1 (en) 1981-08-20
US4189160A (en) 1980-02-19
EP0000517A1 (de) 1979-02-07
JPS5421785U (de) 1979-02-13

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